Rotary piston machine

ABSTRACT

In a rotary piston machine that may serve as an engine or a pump and which has a rotor containing radially disposed cylinders and pistons which are connected by axially disposed working fluid passageways which extend through a control face, the control face passing into suitable alignment as the rotor turns with fluid inlet and outlet ports in the housing; a thrust member about the shaft is adapted to act along the axis of the machine against the rotor to help maintain the seal at the control face and has associated therewith generally circular annular pressure chambers, connecting with the high pressure fluid in the machine and the low pressure fluid in the machine, each of which chambers having large and small portions which are eccentric to the shaft of the machine and are positioned oppositely to each other, the chambers being positioned so that the fluid contained therein exerts an axial thrust against the thrust member with a pressure that is variable and balanced to maintain the optimum sealing force on the control faces.

4 f rs 44mm any! United States Patent [72] [mentor Karl Eickmm 7 3,122,104 2/1964 Byers, .lr 103/161 (V) Hayama 'nachi Kanagawa. 3,! Etckmalin nu ken, Japan 3,398,698 8/1968 Elckmann 103/161 PP 876,177 Primary Examiner-Mark Newman Filed 1969 Assistant Examiner- Wilbur .l. Goodlin Patented 9, 1971 AttorneyBurgess, Dinklage & Sprung [32] Priority Dec. 8, 1966 h [33] Germany v 1 g [31] 8902.10 ABSTRACT: In a rotary piston machine that may serve as an 28311318118631! soflg gplhgzhvoghii s g g-d which engine or a pump and which has a rotor, cor taining radially -i g a 6558; No disposed cylinders and pistons which are connected by axially ii-83 June 4 g disposed working fluid passageways which extend through a control face, the control face passing into suitable alignment as the rotor turns with fluid inlet and outlet ports in the hous- [54] ROTARY PISTON MACHINE 7 ing; a thrust member about the shaft is adapted to act along 7 claims, 22 Drawing Figs the axis of the machine against the rotor to help maintain the seal at the control face and has associated'therewith generally n 91/497 circular annular pressure chambers, connecting with the high [51] Int. Cl. F04b 1/10 pres-sure fluid in the machine and the |ow pressure fl id in the [50] Field of Search 103/ 126L, machine each f which chambers having Mtge and small 161A 161v; 230/177; 91/202 tions which are eccentric to the shaft of the machine and are sitioned o positely to each other, the chambers being posi- [56] References cued and so tha the fluid contained therein exerts an axial thrust UNITED STATES PATENTS against the thrust member with a pressure that is variable and 2,649,740 8/ 1953 Murray et al. 103/ l 26(L) balanced to maintain the optimum sealing force on the control 2,824,523 2/ 1958 Campbell et al l03/l26( L) faces.

5 asis ezil PATENTEUFEB 919m 3.. 561,328

SHEET 3 OF 6 INVENTOR KARL EICKM 1? ATTO EY PAIENIEnrw-m 1 3561.328

samunrs I INVENTOR KARL E/C/(MA/V/V I BY ATTORNEY PREAMBLE This invention is related to improvements in machines of the type with radial variable displacement chambers used as pumps, motors, compressors, engines and transmissions wherein the fluid flow from or into the displacement chambers is substantially in the axial direction. In such machines, the rotor which contains the displacement chambers, cooperates with at least one control body, which is provided with control ports for the transfer of fluid to or away from the rotor.

Mating smooth control faces are provided between the rotor and the control body to permit relative movement between the two. A thin fluid film is maintained between the faces so that the surfaces do not weld together. The control faces are pressed tightly together so that leakage through the clearance remains small.

The problem in such machines, however, is that the pressure of the fluid acting along the axis against the rotor is not in all cases and at all times locationally in suitable balance with the pressure acting from an opposite location of another clearance between the control faces. At some other locations the pressure action from the fluid-containing chamber is too big and from another, too small, so that the fluid film between the control faces tends to have different thickness at different local places.

In machines of this type the size of the bearings or the control body thereof may restrict the adjustment of the stroke of the machine and its displacement volume, thereby limiting the power of the machine.

THIS INVENTION According to this invention the above-mentioned shortcomings are overcome as follows:

A pair of fluid containing chambers are provided at one end of a hearing or thrust member which is movably along the shaft of the machine against the rotor or control body. There is a medial seal between both fluid-containing chambers in the form of a circular ring which is eccentric to a degree about equal to the eccentricity of the machine, i.e., the amount of the inner and outer points of movement of the displacement chambers, in such a way that the chambers have a wide portion and a narrow portion with the wide portion of one being aligned with the narrow portion of the other. The fluid-containing chambers communicate with a high pressure port and a low pressure port on the control face. The wider portion of the high pressure chamber lies substantially in line with the high pressure control port and the smaller portion of the chamber is in line with the low pressure port.

A passage extends from each high pressure port into the wider portion of each of the chambers. Both chambers are sealed from each other. They are, via the passages, automatically filled with fluid which acts against the thrust member in order to press the control faces together. At any instant there will be a wider portion of the fluid-containing chamber aligned with a high pressure control port and a smaller portion of the fluid-containing chamber aligned with a low pressure control port. The invention thereby achieves a suitable balance of the local forces in the areas of the control faces and results in a uniform pressing of the control faces against each other. Safe operation of the machine is thereby, according to this invention, assured.

A second object of the invention is to so configure the cover portions, housing portions, control bodies, thrust member in such a way that a large'displacement stroke in the machine will be permitted so that the power and efficiency of the machine willbecome maximized. This is accomplished by having-the outer faces of the various parts formed with radii around an axis spaced from the main axis thus giving the parts an elliptical shape and permittinga greater adjustment of the stroke, which was heretofore impossible when cylindrical portions and parts were provided in conventional machines.

A third counteracting generally circular annular chamber on the opposite end or shoulder of the thrust bearing can be provided to help adjust or balance the axial forces acting on the rotor. By this means the forces of the first two fluid-containing chambers of the invention can be counterbalanced in an exactly calculated and predetermined manner.

Another object of this invention is to assemble at least two fluid-handling devices one of which may be a pump and the other a motor, in such a manner the shaft of one extends through the other.

A fluid line may extend through the central shaft. If a shaft of a pump so extends through a motor then a differential gear can be provided on the end of the motor and pump shafts and the outgoing shaft of the differential can transfer mechanical power out of the transmission. If pump and motor are at full displacement, the outgoing shaft may stand still, because the motor might revolve contrary to the pump. With the pump at minimum displacement and the motor stopped, the outgoing shaft may be used to transfer power to the pump shaft. If the pump is driven with full eccentricity in another direction, the velocity of the outgoing shaft of the end differential can be doubled.

THE DRAWINGS In the drawings:

FIG. I is a longitudinal sectional view through a fluid-handling device designed according to this invention;

FIG. 2 is a partial cross-sectional view through FIG. 1 taken along the line lI-II;

FIG. 3 is a partial cross-sectional view through FIG. 1 taken along the line III-III;

FIG. 4 is an explanatory schematic combining the features shown in FIGS. 2 and 3;

FIG. 5 is a partial cross-sectional view through FIG. 1 taken along the line V-V;

FIG. 6 is a longitudinal sectional view through another embodiment of the invention wherein a pump and a motor are combined with one extending partially through the other;

FIG. 7 shows a portion of FIG. 6;

FIG. 8 is a longitudinal sectional view along line VIII-VIII of FIG. 7;

FIG. 9 is a cross-sectional view through FIG. 7 taken along the line IX-IX;

FIG. 10 is an explanatory schematic of FIG. 9;

FIG. 11 is a cross-sectional view through FIG. 7 taken partially along the line XI-XI;

FIG. 12 is a cross-sectional view through FIG. 7 taken'partially along the line XII-XII;

FIG. 13 is an explanatory diagram for explaining the arrangement of FIG. 7;

FIG. 14 is a cross-sectional view through FIG. 7 taken partially along the line XIV-XIV;

FIG. 15 is a cross-sectional view of FIG. 6 taken along the line XV-XV;

FIG. 16 is a longitudinal sectional view through another embodiment;

FIG. 17 is a cross-sectional view through FIG. 16 along XVII-XVII;

FIG. 18 is a longitudinal view through another embodiment FIG. 19 is a cross-sectional view through FIG. 18 along IXX-IXX;

FIG. 20 is a longitudinal sectional view through another embodiment of the invention;

FIG. 21 is a cross-sectional view through FIG. 20 taken along the line XXI-XXI;

FIG. 22 is a cross-sectional or longitudinal view through a portion of an assembly in a machine of the invention.

DESCRIPTION Housing 30 of the pump or fluid-handling device of FIG. 1 has covers 12 and 29 which have a pair of fluid passages 858, 860 or 658, 660, respectively, ending in threaded ports 57, 59 or 657, 659, respectively, one-of which is an entrance line and the other is an exhaust line. Rotor l is carried on shaft which is borne in bearings 11 (See FIG. 5) and is movable therein along the axis to a limited extent. Control body 3 with control ports 33 and 34 (See FIG. 3) and control body 4 with similar control ports, one of which is shown at 44 (FIG. I) are placed at each end of rotor 1 Fluid-handling chambers 14 and 15 arranged in two adjacent chamber groups, are provided in rotor 1. Pistons l6 and 17 move therein as the rotor revolves. Pistons l6 and 17 are guided by stroke actuator 24 carried in support ring 26 which in turn is borne in bearings 27. Guideshoes 18 are provided between the actuator 24 and pistons 16 or 17. Ridges 23 in shoes 18, and mating slot 25 in actuator 24 are provided to aid in aligning the members.

A cylindrical thrust member 2 is provided according to this invention on one side of the rotor and is slideably contained within the bore of the housing 12. Control body 4 bears against front cover 29 and the passages through cover 29 communicate to the control ports in control body 4. Rotor passages 19 extend from working chambers 15 in rotor 1, and rotor passages 19 extend from chambers 14, and communicate with the respective control ports of the control bodies 3 and '4. The opposite surface of control body 3 bears against the thrust member 2 and both bodies are movably fixed together to move along the axis of the shaft.

At the opposite end of thrust member 2, two fluid containing chambers 5 and 6 are provided. Passage 3] (shown in FIGS. 2 and 5) and control port 33 (FIGS. 3 and 4) provide a passageway fluid-containing chamber 5 (FIGS. 1 and 2) and passage 32 extends through thrust member 2 from control port 34 FIGS. 2 and 3) into fluid-containing chamber 6 FIGS. 1 and 3).

Fluid-containing chambers 5 and 6 are sealed against each other by seal means 9. They are cylindrically configurated, but the axis of the outer surface of chamber 5 and the inner surface of chamber 6 are spaced from the center axis of the outer surface of chamber 6 and inner surface of chamber 5 by an eccentric distance which is about equal to the stroke-adjustment capability of the machine. The axis of the outer surface of chamber 6 and the inner surface of chamber 5 are aligned with the machines axis. This eccentricity is shown more clearly in FIGS. 2 and 4 by reference number 37. Thus each chamber 5 and 6 forms, according to this invention an enlarged portion in a direction which is normal to the face through the outer and inner displacement deadpoints of the machine, and in the opposite direction thereto a narrow portion. In chambers 5 and 6 the enlarged portions are located oppositely to each other and so are the narrowed portions.

With reference to FIG. 4, reference numbers 35 and 36 demonstrate the closing arcs between the control ports 33 and 34 whenever the rotor passages 19 pass over the inner or outer control ports during displacement. The larger portion of chamber 6, when viewed from flange 13, of control port 34 and the narrower portion of chamber 5 lies in front of control port 34. The larger portion of chamber 5 lies in front of control port 33 and so does the narrower portion of chamber 6. In the middle between the larger and narrower portions of chambers 5 and 6 are two medial portions of about equal size and they lie in front of closing arc 35 and 36 respectively. As shown in FIG. 4 the larger portion of chamber 5 is considerably larger in area than the opening of port 33 such that the fluid therein acts on member 2 and presses it against body 3 and rotor l, with a small amount of force on the right and left side of member 2 (as illustrated in FIG. 4). The same applies to the other side of FIG. 4, where a large portion of chamber 6 covers port 34 with a similar result. Thus, according to this structure of the invention, because of the fluid contained in space 5 or 6, member 2, and thereby the respective control bodies, will at all times be about equally pressed against the neighboring body or surface with a force that is in excess of the counter acting thrust occasioned by the fluid contained in passageways 19, which force will automatically vary with the fluid pressure required to be contained in the chambers. Therefore, safe operation of the machine is aided by maintaining a unifonn film thickness of fluid on the faces of the control bodies 3 and 4.

The bigger the diameter of bearings 27, the greater is the friction loss because of the bearings, and the efficiency of the machine is reduced. The bearings 27 and their support rings 26 are therefore made as small in diameter as possible. As the adjustment device of the machine moves the stroke adjustment means 28 and stroke actuators upwards or downwards in FIG. 1, or, in other words, as the eccentricity of actuator 24 is increased, the inner faces of rings 26 will tend to touch against the outer faces of the respective cylindrical portions within the inner space of the ring 26. A further increase of eccentricity and stroke is thus not possible.

According to this invention as can be understood from FIG. 5, the outer faces of parts or portions within the inner space defined by ring means 26, i.e., the respective control bodies 3 and 4 and portions of cover 29 and a portion of thrust member 2, are flattened or made elliptical in cross section in such a way as to give more room for movement of the stroke adjustment means 28. The outer surfaces of these parts are formed with a radius on a line which is displaced, see reference numbers 38 and 39, from the center line of the respective part. Face 777 is an arcuate surface of member 2 having a radius on line 39, and face 778 is an arcuate surface having a radius on line 38. Faces 777 and 778 have the configuration of the inner face 779 of ring 26. The result that the inner face 779 can now be moved closer to the axis of the machine. The stroke and displacement volume, and the power, of the new machine is thereby greatly increased. In actual design, this increase of stroke, displacement and power can amount up to 40 percent. At the same time the weight of the machine can be decreased because the diameter of the bearings can be kept small as can the weight of the neighboring parts.

Referring to FIG. 6, it is possible to extend a shaft of one of the machines through another one. Two fluid-handling devices, have the same axis and are mounted in line with one another. One acts preferably as a pump on the left side of FIG. 6, and the other as a motor on the right, or, they together form a transmission. The same reference numbers are used in FIG. 6 as are used in FIGS. 1 to 5 to identify similar parts except that in the case of the left side of FIG. 6, the number is in the s and the case of the right side of FIG. 6, the number is in the 2 to 3 hundreds. Pump 101 is a radial piston pump, while motor 201 is a vane-type motor. Shaft 149 of motor 201 is provided with a rotor hub or center bore 148 which extends through the whole length of the shaft 149. The displacement chambers 114, 115, 314 and 315 are located radially about shaft 149 as are the pistons 116, 117, 216 and 217 and the stroke actuators.

It is possible to take the transmission of the power either from shaft 147 which has one velocity, or to take the power from the motor shaft 149 which may have any other velocity, torque or rotation direction depending on the stroke of the pump and motor. It is even possible to take fluid power from passage 146 through shaft 147. An additional shaft could extend through bore 146. Such a shaft, not shown in the drawing, could be used for power transfer or for transfer of a command control or the drive of a control pump, or the like.

A differential gear can be placed on the end of the transmission. One shaft, for example, the motor shaft, would then drive one ingoing rotary member of the differential and the pumpshaft or shaft 147, extending through, could drive the other ingoing rotary member of the differential gear. The outgoing shaft or outgoing rotatable member of the differential gear would then have different torque and revolution, depending not solely on the rotational movement of the pump shaft but on the combination of the motion, whether at rest or not, of pump shaft 147 and motor shaft 149.

Member 245 is located in the middle between pump 101 and motor 201 and it can move along the axis to a limited extent to allow the rotors and control bodies of the pump and motor to be suitably held together or pressed together by the fluid-containing chambers 105 and 106, positioned on the left end of thrust member 2. Media] member 245 and housing 112 may be provided with passages 161, 162, 163 and 164 (See FIG. 15) for the transfer of fluid from pump 101 to motor 201 and vice versa.

Passages 161 and 162 extend through the medial member 145 (in FIG. 15) which is prevented from rotation by key 165. One of the passages 161 and 162 is a passage for passing fluid from the pump to the motor and the other for passing fluid from the motor back to the pump. Passages 163 and 164 extend from the pump through the housing 112 to the motor and one acts to pass fluid from the pump to the motor and the other acts to transfer fluid from the motor to the pump. These passages through housing 112 can serve to cool the fluid.

An alternative embodiment of the invention is illustrated in FIGS. 7 to 14. FIG. shows, in a manner similar to FIG. 4, a schematic of the two fluid-containing chambers 105 and 106. Reference number 108 shows the circular inner face of chamber 105 and reference 107 shows the circular outer face of chamber 106. Faces 107 and 108 are concentric. The medial sealing face 109 between chambers 105 and 106 is eccentric to faces 107 and 108. The eccentricity is cited by reference number 137 and e. As a result of this eccentricity, the chambers 105 and 106 form a narrow portion and a wider portion and the respective narrow and wide portions of the two chambers are oppositely located.

For design reasons, it is desirable to extend a portion 155 of housing 112 towards the rotor of the machine in order to have it carry the shaft bearings 111. Such bearings must have a certain minimum diameter which tends to limit the size of the fluid-containing chambers 105 and 106. If the cross-sectional area of the fluid-containing chambers 105 and 106 were to small the machining of them would be difficult. If the radial dimensions through the fluid-containing spaces 105 and 106 are too large, however, with a too large of a cross-sectional area, the pressing force along the axis by the fluid in the chambers can be too great.

It is therefore desirable, in accordance with this invention, to provide a means for counteracting the fluid force ocassioned by the fluid contained in chamber 105 and 106. To achieve this, a fluid-containing counterbalancing chamber 140 and/or a closure member 144 is disposed to act oppositely thereto. A passage is provided to transfer fluid into said chamber 140. As will be seen from FIGS. 7 and 8, a shoulder is provided on member 102, against which fluid chamber 140 can act.

The outer face and also the inner face of fluid-containing counteracting chamber 140 can be circular to simplify its manufacture. Seals 141 can be provided. Cover means 144, for chamber 140 can also be concentric and circularly enclose chamber 140 in one axial direction. Cover 144 may be retained in housing 112 by suitable retainingmeans. Thus, thrust member 102 can move to a little extent along the axis between chambers 105 and 106, and 140, thereby enabling it to move more closely to the rotor 101 or away therefrom within the limits of the axial extensions of the chambers 105, 106 and 140. Passage body 102 can be hollow to permit cover portion 155 to extend into it and retain bearings 111 and shaft 110 (FIG. 8). A passage means and fluid chamber 154 for transferring of fluid out of one of the chambers 105, 106 or 140 through shaft 110 and into passage 142 therein can be provided, especially for automatic control purposes.

FIG. 9 shows fluid containing chambers 105 and 106 with passages 160 and 158 which extend through member 102. In FIG. 13 the dotted line 241 shows the inner face of the counteracting chamber 140. In order to determine the axial thrust of chamber 105 or 106, it is necessary to determine the difference between the areas encompassed by face 141 and face 107, i.e., the cross-sectional area of chamber 105 or 106 minus the effective cross-sectional area of counteracting chamber 140.

Because the medial seal 109 between chambers 105 and 106 is eccentric, as shown in FIG. 13, there are overlapping cross-sectional areas 240, 540, 440, 740, 340, 640, 840 and 940 so dimensioned that they appropriately cover like closing arcs, different areas of the control faces and the control ports therein. Thus, a fluid pressure balance can be realized over the entire area of the control ports and control faces to aid in the control of the fluid clearances of the machine.

In FIG. 11 the locations of passages 133 and 134 through control body 3 (FIG. 1) are illustrated. Also, shown are closing arcs and the pins 43 for preventing rotation of control body 3. FIG. 11 also shows how shaft is located inside of thrust member 2 and the location of passage 142 inside of shaft 110. It should also be recognized that there are ribs between the portions of the control ports 133 and 134 in order to maintain the radial stability and total rigidity of the control bodies.

FIG. 12 illustrates in cross section the location of the rotor passages 119 from chambers 14 (FIG. 1) in the rotor 101.

FIG. 14 shows in cross section view how the outer faces and the control passageways of thrust member 2 (or 102) are formed in order to accommodate its elliptical shape. It is desirable to locally divide passageways 131 and 132 by ribs as shown. These ribs help provide the requisite radial and overall stability and rigidity. The respective portions of passages 13] and 132 come together at the ends of the thrust member to form single outlet or inlet.

FIGS. 7 and 8 illustrate that bearing 111 is positioned between port on of housing or cover 112 and extends along the axial for the purpose of providing a guide or hearing portion for bearing one end of thrust member 102 (or 2) and guide the same. The thrust member is further supported by faces on member 155 or 112 at its other end.

In FIGS. 16 and 17 it is demonstrated how, according to another object of the invention, a fluid-containing thrust bearing 478 can be provided on one end of a rotor 40] for pressing it against a control means 403 on the other axial end thereof. Passage 476 provides the means for filling chamber 478 with the necessary fluid. Thrust member 401 and chambers 480, 481 provide the necessary axial thrust to the rotor 401 and the control body 403, which thrust is counteracted by the fluid in space 478. On the lower portion, as illustrated (FIG. 16) a chamber 477 may be locally provided for acting like chamber 478 but on the other half of the machine. Extensions 495, 494, 496 and 497 (FIG. 17) are provided in accordance with this invention in order to cover suitable different areas in a balanced manner. Passages, like 491, 490, 493, fluid pockets like 492 etc. are provided to transfer fluid into the radial fluidtype thrust bearings or other fluid-containing chambers or recesses thereof, as, for example, as shown by references 169, 470, 473, etc. Passages 472 can also be provided for lubricating purposes.

In FIG. 18 and 19 it is shown how chambers 99 and 96 are provided in order to press rotor 1 in an axial direction against a control member 3. Chambers 99 and 96 are closed by members 531 or 97. Member 97 or member 531 are borne by axial thrust member 694. They are rotatable. The axial thrust given by chambers 99 and 96 against bodies 531, 97 and 694 can be quite high and the slide bearings may not be strong enough to take the axial forces. For roller or ball bearings there is usually not enough space to make them large enough, in accordance with this invention, to a fluid balancing chamber 94 is provided at the end of member 97. Passages 95 are used to pass fluid to chamber 94. Body 97 is borne in bearings 593 for a suitable rotational movement.

FIGS. 20 and 21 show that to seal chamber 5 from chamber 6 a circular, groove 87 can be formed in thrust member 2 eccentrically to faces 7 and 8. A seal member 84 is inserted into groove 87, extends axially thereout and is pressed by fluid force in chamber 87 against face 567 of body 12. This simplities the manufacture of spaces 5 and 6 and the like. Pressure relieving spaces 88 are provided on one end of seal 84 and passages 85 or 86 which can contain check valves, transfer fluid under pressure into space 87. Groove 87 can be placed in passage body 2 (or 102) as shown or can be located in housing 12 (or 112).

FIG. 22 shows a control cylinder 89 with a reciprocating control piston 90 therein which alternatively. depending on pressure in passageways 92 and 93, opens or closes the access of these passageways to passage 91. Passage 92 and 93 can lead directly or indirectly to different control ports or fluidcontaining chambers or 6 in the machine and passage 91 can lead to a space in the machine which is to contain at all times the highest fluid pressure existing in the machine. For example, passage 91 can lead to space 87 of FIG. 20.

I claim:

1. In a fluid-handling device having:

a. a rotor having on one end a radially disposed rotor control face;

b. a shaft supporting said rotor for rotation;

c. a fixed housing about said rotor and mounting said shaft for rotation therein; said housing having a housing control face mating with said rotor control face;

d. fluid handling chambers, each with an actuating member, associated with said rotor and adapted to intake and expel a working fluid synchronously with the rotation of said rotor;

e. actuating means disposed about said rotor in said housing and adapted to effect sequential inward and outward motion of said actuating member as said rotor rotates; inlet and outlet housing passageways axially extending through said control faces and adapted to supply fluid to and to remove fluid expelled from said chambers;

g. rotor passageways one for each chamber and communicating with said rotor control face; the improvement which comprises:

h. a radial thrust member about said shaft and acting against said rotor in a direction towards said rotor in the direction of said control face;

. two generally circular annular chambers about said shaft adapted to contain fluid under pressure, one of which, the high pressure chamber, communicates with a source of high pressure fluid in said device and the other, the lower pressure chamber, communicating with a source of lower pressure fluid in said device, said chambers having large and small portions eccentric to said shaft and oppositely disposed to each other and said circular annular chambers being positioned so that the fluid contained therein acts on and exerts an axial thrust against said thrust member.

. In a rotary piston machine having:

. a rotor having radially disposed cylinders and on one end a radially disposed rotor control face;

b. a shaft supporting said rotor for rotation;

c. a fixed housing about said rotor and mounting said shaft for rotation therein; said housing having a housing control face mating with said rotor control face;

d. pistons within said cylinders;

e. piston actuating means disposed about said rotor in said housing and adapted to effect sequential inward and outward motion of said pistons as said rotor rotates;

f. inlet and outlet housing passageways axially extending through said control faces and adapted to supply fluid to and to remove fluid expelled from said cylinders;

g. rotor passageways one for each cylinder and commu: nicating with said rotor control face; the improvement which comprises:

h. a radial thrust member about said shaft and acting against said rotor in a direction towards said rotor in the direction of said control face;

i. two generally circular annular chambers about said shaft adapted to contain fluid under pressure, one of which, the high pressure chamber, communicates with a source of high pressure fluid in said machine and the other, the lower pressure chamber, communicating with a source of lower pressure fluid in said machine, said chambers having large and small portions eccentric to said shaft and oppositely disposed to each other and said chambers being positioned so that the fluid contained therein acts on and exerts an axial thrust against said thrust member. 3. The machine of claim 2 wherein said thrust member IS elliptical in cross section so as to permit greater adjustment of said piston actuating means.

4. The machine of claim 2 wherein said chambers are contiguous and are separated by a medial seal means with a central opening that is eccentric to said chambers and to said shaft.

5. The machine of claim 2 wherein an annular control body with control faces and control passageways is interposed between said rotor and said housing and is acted upon by said thrust member.

6. The machine of claim 2 wherein two such machines are located in a common axial centerline and said shaft of one at least in part within the shaft of the other.

7. The machine of claim 2 wherein a third generally circular counterbalancing chamber is disposed to exert because of fluid contained therein axial force on said thrust member in a direction away from said rotor, said counterbalancing chamber communicating with a source of fluid under pressure in said machine. 

1. In a fluid-handling device having: a. a rotor having on one end a radially disposed rotor control face; b. a shaft supporting said rotor for rotation; c. a fixed housing about said rotor and mounting said shaft for rotation therein; said housing having a housing control face mating with said rotor control face; d. fluid handling chambers, each with an actuating member, associated with said rotor and adapted to intake and expel a working fluid synchronously with the rotation of said rotor; e. actuating means disposed about said rotor in said housing and adapted to effect sequential inward and outward motion of said actuating member as said rotor rotates; f. inlet and outlet housing passageways axially extending through said control faces and adapted to supply fluid to and to remove fluid expelled from said chambers; g. rotor passageways one for each chamber and communicating with said rotor control face; the improvement which comprises: h. a radial thrust member about said shaft and acting against said rotor in a direction towards said rotor in the direction of said control fAce; i. two generally circular annular chambers about said shaft adapted to contain fluid under pressure, one of which, the high pressure chamber, communicates with a source of high pressure fluid in said device and the other, the lower pressure chamber, communicating with a source of lower pressure fluid in said device, said chambers having large and small portions eccentric to said shaft and oppositely disposed to each other and said circular annular chambers being positioned so that the fluid contained therein acts on and exerts an axial thrust against said thrust member.
 2. In a rotary piston machine having: a. a rotor having radially disposed cylinders and on one end a radially disposed rotor control face; b. a shaft supporting said rotor for rotation; c. a fixed housing about said rotor and mounting said shaft for rotation therein; said housing having a housing control face mating with said rotor control face; d. pistons within said cylinders; e. piston actuating means disposed about said rotor in said housing and adapted to effect sequential inward and outward motion of said pistons as said rotor rotates; f. inlet and outlet housing passageways axially extending through said control faces and adapted to supply fluid to and to remove fluid expelled from said cylinders; g. rotor passageways one for each cylinder and communicating with said rotor control face; the improvement which comprises: h. a radial thrust member about said shaft and acting against said rotor in a direction towards said rotor in the direction of said control face; i. two generally circular annular chambers about said shaft adapted to contain fluid under pressure, one of which, the high pressure chamber, communicates with a source of high pressure fluid in said machine and the other, the lower pressure chamber, communicating with a source of lower pressure fluid in said machine, said chambers having large and small portions eccentric to said shaft and oppositely disposed to each other and said chambers being positioned so that the fluid contained therein acts on and exerts an axial thrust against said thrust member.
 3. The machine of claim 2 wherein said thrust member is elliptical in cross section so as to permit greater adjustment of said piston actuating means.
 4. The machine of claim 2 wherein said chambers are contiguous and are separated by a medial seal means with a central opening that is eccentric to said chambers and to said shaft.
 5. The machine of claim 2 wherein an annular control body with control faces and control passageways is interposed between said rotor and said housing and is acted upon by said thrust member.
 6. The machine of claim 2 wherein two such machines are located in a common axial centerline and said shaft of one at least in part within the shaft of the other.
 7. The machine of claim 2 wherein a third generally circular counterbalancing chamber is disposed to exert because of fluid contained therein axial force on said thrust member in a direction away from said rotor, said counterbalancing chamber communicating with a source of fluid under pressure in said machine. 